US20020108458A1 - Multiple-speed gear arrangement for power tools - Google Patents
Multiple-speed gear arrangement for power tools Download PDFInfo
- Publication number
- US20020108458A1 US20020108458A1 US09/782,453 US78245301A US2002108458A1 US 20020108458 A1 US20020108458 A1 US 20020108458A1 US 78245301 A US78245301 A US 78245301A US 2002108458 A1 US2002108458 A1 US 2002108458A1
- Authority
- US
- United States
- Prior art keywords
- gear
- output
- output shaft
- actuator
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B27—WORKING OR PRESERVING WOOD OR SIMILAR MATERIAL; NAILING OR STAPLING MACHINES IN GENERAL
- B27C—PLANING, DRILLING, MILLING, TURNING OR UNIVERSAL MACHINES FOR WOOD OR SIMILAR MATERIAL
- B27C1/00—Machines for producing flat surfaces, e.g. by rotary cutters; Equipment therefor
- B27C1/02—Smoothing, i.e. working one side only
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19023—Plural power paths to and/or from gearing
- Y10T74/19074—Single drive plural driven
- Y10T74/19079—Parallel
- Y10T74/19084—Spur
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19237—Internal-external gears
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19284—Meshing assisters
- Y10T74/19288—Double clutch and interposed transmission
Definitions
- the invention relates to power tools and, in particular, to a multiple-speed gear arrangement for a planer.
- thickness planers i.e. planers for reducing the thickness of a piece of wood or similar materials while providing a smooth and flat finish
- Such portable planers balance the need to provide the required power to produce a smooth finish with the need to conserve space and decrease weight for portability.
- One planer such as the model Delta 22-560 planer manufactured by Delta International Machinery Corp. of Jackson, Tenn., has a 15-amp motor and a cutterhead speed of 8000 rpm. This planer is capable of handling stock of up to 121 ⁇ 2 inches wide.
- the feed rate of the workpiece is controlled by the speed of the infeed and outfeed rollers, which is typically, about 26 feet/minute.
- An electric motor drives the cutterhead by means of a belt and pulley system.
- the cutterhead provides input to a speed reduction gearbox, and the output speed of the gearbox drives the feed rollers by means of a chain and sprocket arrangement.
- One embodiment of the invention includes a multiple-speed gearbox, preferably for a planer, but also for other power tools.
- Another embodiment of the invention comprises a planer that includes a cutterhead that is mounted on an input shaft, which is driven by an electric motor.
- the planer further includes an infeed and an outfeed roller, which are driven by an output shaft.
- One embodiment of the gearbox includes a first input gear that is mounted on a first axis and that is rotatable by the input shaft. This embodiment further includes first and second output gears mounted on the output shaft such that they may rotate independently about the output shaft.
- the gearbox further includes a three-gear set that is rotatable about a second axis that is parallel to the input shaft.
- the three-gear set has a middle gear, a first outer gear and a second outer gear.
- the middle gear engages the first input gear
- the first outer gear engages the first output gear
- the second outer gear engages the second output gear.
- the input shaft drives the first input gear through a two-gear set.
- An actuator is attached to the output shaft to selectively engage the output shaft with the first output gear to provide a first output speed or with the second output gear to provide a second output speed.
- the output shaft drives the infeed and outfeed rollers with the first or the second speed, depending upon which outer gear is engaged with the output shaft.
- the actuator may also have a neutral position.
- the described arrangement of the gears makes the gearbox compact, so that it may be supported between two gear plates separated by a distance of about three centimeters.
- the gearbox may also be used for other power tools, for example a planer/shaper or a molder.
- FIG. 1( a ) is a front, bottom and left side isometric view of the driving components of a planer of the subject invention that also includes an embodiment of a gearbox of the invention;
- FIG. 1( b ) is a rear, top and right side isometric view of the driving components of the planer of FIG. 1( a );
- FIG. 2 is a side view of the gearbox employed in the planer driving components depicted in FIG. 1( a );
- FIG. 3 is a cross-sectional view of the gearbox taken along section III-III of FIG. 2 at a first position of gear engagement;
- FIG. 4 is a cross-sectional view of the gearbox taken along section IV-IV of FIG. 2 at a second position of gear engagement;
- FIG. 5 is an exploded assembly view of the components of an embodiment of a three-gear set with the integral gear assembly 157 shown in cross section;
- FIG. 6( a ) is a side view of an embodiment of an actuator of the present invention.
- FIG. 6( b ) is an end view of the actuator of FIG. 6( a );
- FIG. 7( a ) is a sectional side view of an embodiment of an output shaft of the present invention.
- FIG. 7( b ) is a cross-sectional view along axis VII(b)-VII(b) of FIG. 7( a );
- FIG. 8( a ) is a side view of an embodiment of a tab of the present invention.
- FIG. 8( b ) is an end view of the tab of FIG. 8( a );
- FIG. 9( a ) is a front view of an embodiment of a first output gear of the present invention.
- FIG. 9( b ) is a sectional side view taken along line IX(b)-IX(b) in FIG. 9( a );
- FIG. 10( a ) is a front view of an embodiment of a second output gear
- FIG. 10( b ) is a sectional side view taken along line X(b)-X(b) in FIG. 10( a );
- FIG. 11 is a partial perspective view of detail B of FIG. 9( a );
- FIG. 12 is a partial perspective view of detail C of FIG. 10( a );
- FIG. 13 is a perspective view of an embodiment of a rack of the present invention.
- FIG. 14 is a side view of an embodiment of a rack-and pinion assembly of the present invention.
- FIGS. 1 ( a ) and ( b ) are isometric views of the driving components of a portable planer 40 and their connections according to one embodiment of the invention.
- a motor 50 drives, by means of belt and pulley system generally designated 70 , an input shaft 65 on which a conventional cutterhead 60 is mounted, either as an integral piece, or as a separate component.
- the input shaft 65 provides input to a multiple-speed gearbox 80 .
- an output speed is transmitted to a first feed roller 90 through a first sprocket and chain system generally designated as 95 .
- the first feed roller 90 is the outfeed roller.
- a second sprocket and chain system generally designated as 105 transmits the same output speed from the first feed roller 90 to a second feed roller 100 .
- An actuator 115 operates a tab 165 (shown in FIG. 3) that moves in one of two positions corresponding to a first or second output speed.
- the tab 165 may also have a neutral position, whereat no output speed is provided.
- the movement of the tab 165 is controlled by a rack and pinion assembly 120 , which is connected to the actuator 115 .
- the gearbox 80 is supported between a first plate 130 and a second plate 132 , which are separated by a plurality of spacers 145 .
- Each spacer 145 comprises a hollow pin 146 that has a capscrew 147 extending therethrough to be threadedly received in a threaded bore 149 in plate 132 .
- a first input gear 170 may be integrally formed with a first shaft stem 178 that is rotatably supported in a bearing sleeve 179 pressed into a hole 133 in the second plate 132 and a second shaft stem 181 that is rotatably supported in a bearing sleeve 185 that is pressed into hole 183 in the first plate 130 . See FIG. 3.
- Shaft stem 178 defines a first axis 148 .
- a second input gear 175 is also keyed on the first shaft stem 178 so that the first input gear 170 and the second input gear 175 rotate with the same speed about the first axis 148 . It will be appreciated that other methods of connecting the first input gear 170 and the second input gear 175 are within the purview of the person of ordinary skill in the art.
- a third input gear (drive gear) 182 is attached to the input shaft 65 and meshingly engages the second input gear 175 .
- the number of teeth of the first input gear 170 , the second input gear 175 and the third input gear 182 are n 1 , n 2 , n 3 respectively. Denoting the speed of the input shaft by ⁇ is , the common speed of the first input gear 170 and the second input gear 175 is (n 3 /n 2 ) ⁇ is .
- the first input gear 170 engages the middle gear 158 of a three-gear set generally designated as 160 .
- the three-gear set 160 includes a first outer gear 155 and a second outer gear 150 .
- the second outer gear 150 includes a third shaft stem 159 .
- the first outer gear 155 and the middle gear 158 may comprise an integral assembly 157 , which is attached to the third shaft stem 159 to form the three-gear set 160 . See FIG. 5.
- This arrangement results in a common rotational speed for all three gears of the three-gear set 160 about a second axis 162 , and is one of many arrangements that may be used to achieve the same effect. Denoting by n m the number of teeth of the middle gear 158 of the three-gear set, the speed of the three-gear set ⁇ im , which is defined as the input speed ⁇ im , is
- ⁇ im ( n 1 /n m )( n 3 /n 2 ) ⁇ is
- the first outer gear 155 engages a first output gear 135 and the outer gear 150 engages a second output gear 137 so that when the input shaft 65 rotates with a speed ⁇ is , the first output gear 135 rotates with a speed ⁇ o1 and the second output gear 137 rotates with good speed ⁇ o2 :
- n 1m is the number of teeth of the first outer gear 155
- n 2m is the number of teeth of the second outer gear 150
- n o1 is the number of teeth of the first output gear 135
- n o2 is the number of teeth of the second output gear 137 .
- a kinematic requirement for gear engagement is satisfied when the number of teeth is chosen to satisfy the following equation:
- n o1 +n 1m n o2 +n 2m ,
- the first output gear 135 and the second output gear 137 are mounted on an output shaft 138 so that they may rotate independently about the output shaft 138 .
- the output shaft 138 may rotate with a first speed equal to ⁇ o1 when it is engaged with the first output gear 135 , as shown in FIG. 3, and with a second speed equal to ⁇ o2 when it is engaged with the second output gear 137 , as shown in FIG. 4.
- the output shaft 138 has a first shaft portion 139 upon which an output sprocket 140 may be keyed.
- the first shaft portion 139 is rotatably supported by a conventional bearing 142 that is pressed into a boss 131 formed in the first plate 130 .
- the output shaft 138 further has a second shaft portion 141 that is rotatably supported in a flanged bearing 143 that is pressed into hole 133 in the second plate 132 .
- a gear shifting mechanism which includes an actuator 115 and a tab 165 , as shown in FIGS. 3, 4 and 6 - 8 .
- a first end 188 of the actuator 115 is slidably inserted into a cylindrical bore 190 coaxially provided in the output shaft 138 .
- the actuator 115 is slidably restrained in the bore 190 by the tab 165 , which is fitted through an opening 192 in the first end 188 of the actuator 115 so that the tab 165 forms a right angle with the axis 194 of the actuator 115 . See FIG. 6( a ).
- the tab 165 passes through and extends transversely outward from two diametrically opposed longitudinal slots 186 in the output shaft 138 , the slots 186 being aligned with the opening 192 of the first end 188 of the actuator 115 . See FIGS. 3 and 4.
- the tab 165 may fit into a diametrical slot 194 formed in the hub 200 of the first output gear 135 by two semi-cylindrical first segments 198 , as shown in FIGS. 9 ( a ) and ( b ).
- the top surface 202 of each of the semi-cylindrical first segments 198 forms a first spiral ramp generally designated as 201 , so that moving in a counterclockwise direction along the top surface 202 from one segment to the other (represented by arrow “D” in FIG. 11), there is a ramp-down step 204 (a step in a direction away from the second output gear and toward the first output gear), as shown exaggeratingly in FIG. 11, which is a perspective view of detail B of FIG. 9( b ).
- the tab 165 may similarly fit into a diametrical slot 196 formed in the hub 206 of the second output gear 137 by two semi-cylindrical segments 208 , as shown in FIGS. 10 ( a ) and ( b ).
- the top surface 210 of each semi-cylindrical segments 208 forms a second spiral ramp generally designated 209 , so that moving in a counterclockwise direction along the top surface 210 from one segment to the other (represented by arrow “E” in FIG. 12), there is a ramp-up step 212 (a step in a direction away from the first output gear and toward the second output gear), as shown exaggeratingly in FIG. 12, which is a perspective view of detail C in FIG. 10( b ).
- the spiral ramps 201 and 209 in the hubs 200 and 210 , respectively, of the first and second output gears 135 , 137 facilitate the engagement of the tab 165 with the respective slots 194 and 196 by virtue of the axial actuation of the actuator 115 .
- the actuator 115 is axially moved in a first direction represented by arrow “F” in FIG. 3 the tab 165 contacts the first spiral ramp 201 .
- the second output gear 137 is non-rotatably affixed to the output shaft 138 . It will be appreciated that other methods of shifting between the first and second output gears could be employed without departing from the spirit and scope of the present invention.
- the arrangement of the various gears is such that the gearbox 80 is compact in size with all the gears confined between the first and second gear plates 130 and 132 .
- the gear plates are about three centimeters apart.
- an output sprocket 140 is keyed onto output shaft 138 .
- a first drive chain 97 is received on the output sprocket 140 and on a first sprocket 99 that is keyed on to the shaft of the first feed roller 90 .
- the output sprocket 140 , the first drive chain 97 and the first sprocket 99 form the first sprocket and chain system 95 .
- a second sprocket and chain system 105 includes an second sprocket 102 keyed onto the shaft of the first feed roller 90 , a third sprocket 103 keyed onto the shaft of the second feed roller 100 and a second drive chain 104 received on the second and third sprockets 102 and 103 . See FIG. 1( a ).
- the gears of the gearbox may be molded from a plastic material, which as will be appreciated can provide advantages of sound and weight reduction, or, alternatively, may be custom-made from powdered metal or cut metal, for superior strength and wear.
- the speed reduction ratio in the gearbox is:
- the second (low) speed For an input shaft speed, ⁇ is , of 8000 rpm, for example, the first output speed is about 80 rpm and the second output speed is about 56 rpm. With ordinary materials and applications the output shaft would operate at the higher first speed, which is 80 rpm in this example. When the workpiece is made of harder wood, such as, for example, maple or hickory, or when a better finish is desirable the output shaft speed is shifted down to the second (low) speed, which is 56 rpm in this example. In this example, the speed of the output shaft may be reduced by approximately 30%.
- additional speed reduction from the output shaft to the first feed roller may be provided by using sprockets of unequal size in the first sprocket and chain system 96 , which transmits rotational motion from the output shaft 138 to the first feed roller 90 .
- the additional reduction may be, for example, at a ratio of 8:11.
- the actuator 115 may be manually operated using a handle 222 connected to a rack-and-pinion assembly 120 , as shown in FIGS. 1 ( a ), 1 ( b ), 13 and 14 .
- the rack 125 is a cylindrical sleeve that is riding on the actuator 115 and prevented from sliding off by a screw or retaining ring at one end.
- On one side of the surface of the rack 125 there is a series of rack teeth 214 for engaging the teeth of a pinion 220 .
- three grooves 216 may be provided, each groove corresponding to one of the three positions of the actuator 115 , i.e. the first position of engagement, the second position of engagement and the neutral position.
- a spring-biased plunger 218 may be used to secure the position of the actuator 115 from accidental disengagement.
- a handle 222 is attached to the pinion 220 and is used to advance the rack 125 and the actuator 115 , and the plunger 218 locks the actuator in the desired position. It may be appreciated that other means of controlling and locking the motion of the actuator are within the purview of the person of ordinary skill in the art.
- the multiple-speed gearbox 80 has been described in connection with a portable planer, but it can be readily used with a combination planer/shaper, planer/molder, planer/sander, or with any other portable power tool in which a multiple-speed output is desirable.
- the input shaft is generally driven by a motor and the output shaft drives a tool holder, which is specific to the particular power tool.
Abstract
Description
- 1. Field of the Invention
- The invention relates to power tools and, in particular, to a multiple-speed gear arrangement for a planer.
- 2. Description of the Invention Background
- Over the years, in response to consumer demand, thickness planers, i.e. planers for reducing the thickness of a piece of wood or similar materials while providing a smooth and flat finish, have been decreasing in size. Such portable planers balance the need to provide the required power to produce a smooth finish with the need to conserve space and decrease weight for portability.
- One planer, such as the model Delta 22-560 planer manufactured by Delta International Machinery Corp. of Jackson, Tenn., has a 15-amp motor and a cutterhead speed of 8000 rpm. This planer is capable of handling stock of up to 12½ inches wide. The feed rate of the workpiece is controlled by the speed of the infeed and outfeed rollers, which is typically, about 26 feet/minute. An electric motor drives the cutterhead by means of a belt and pulley system. The cutterhead provides input to a speed reduction gearbox, and the output speed of the gearbox drives the feed rollers by means of a chain and sprocket arrangement.
- It is known that harder materials typically require lower feed rates to enable the cutterhead to produce a smooth finish. Such lower feed rates produce a greater number of cuts per inch, which ultimately results in a smoother surface as compared to faster feed rates, which cause fewer cuts per inch resulting in a rougher surface. Because the overall size of the planer is an important consideration, such planers are equipped with gearing that permits the feed rollers to operate at a single speed. Such gearing arrangements cannot be adjusted to accommodate materials of different hardnesses.
- There remains, therefore, a need for a gear arrangement for a planer that overcomes the limitations, shortcomings and disadvantages of other portable planers without compromising their advantages.
- The invention meets the identified needs, as well as other needs, as will be more fully understood following a review of this specification and drawings.
- One embodiment of the invention includes a multiple-speed gearbox, preferably for a planer, but also for other power tools. Another embodiment of the invention comprises a planer that includes a cutterhead that is mounted on an input shaft, which is driven by an electric motor. The planer further includes an infeed and an outfeed roller, which are driven by an output shaft.
- One embodiment of the gearbox includes a first input gear that is mounted on a first axis and that is rotatable by the input shaft. This embodiment further includes first and second output gears mounted on the output shaft such that they may rotate independently about the output shaft. The gearbox further includes a three-gear set that is rotatable about a second axis that is parallel to the input shaft. The three-gear set has a middle gear, a first outer gear and a second outer gear. The middle gear engages the first input gear, the first outer gear engages the first output gear, and the second outer gear engages the second output gear. The input shaft drives the first input gear through a two-gear set.
- An actuator is attached to the output shaft to selectively engage the output shaft with the first output gear to provide a first output speed or with the second output gear to provide a second output speed. The output shaft drives the infeed and outfeed rollers with the first or the second speed, depending upon which outer gear is engaged with the output shaft. The actuator may also have a neutral position.
- The described arrangement of the gears makes the gearbox compact, so that it may be supported between two gear plates separated by a distance of about three centimeters. The gearbox may also be used for other power tools, for example a planer/shaper or a molder.
- Other features and advantages of the invention will become apparent from the detailed description of the preferred embodiments and from the claims.
- FIG. 1(a) is a front, bottom and left side isometric view of the driving components of a planer of the subject invention that also includes an embodiment of a gearbox of the invention;
- FIG. 1(b) is a rear, top and right side isometric view of the driving components of the planer of FIG. 1(a);
- FIG. 2 is a side view of the gearbox employed in the planer driving components depicted in FIG. 1(a);
- FIG. 3 is a cross-sectional view of the gearbox taken along section III-III of FIG. 2 at a first position of gear engagement;
- FIG. 4 is a cross-sectional view of the gearbox taken along section IV-IV of FIG. 2 at a second position of gear engagement;
- FIG. 5 is an exploded assembly view of the components of an embodiment of a three-gear set with the
integral gear assembly 157 shown in cross section; - FIG. 6(a) is a side view of an embodiment of an actuator of the present invention;
- FIG. 6(b) is an end view of the actuator of FIG. 6(a);
- FIG. 7(a) is a sectional side view of an embodiment of an output shaft of the present invention;
- FIG. 7(b) is a cross-sectional view along axis VII(b)-VII(b) of FIG. 7(a);
- FIG. 8(a) is a side view of an embodiment of a tab of the present invention;
- FIG. 8(b) is an end view of the tab of FIG. 8(a);
- FIG. 9(a) is a front view of an embodiment of a first output gear of the present invention;
- FIG. 9(b) is a sectional side view taken along line IX(b)-IX(b) in FIG. 9(a);
- FIG. 10(a) is a front view of an embodiment of a second output gear;
- FIG. 10(b) is a sectional side view taken along line X(b)-X(b) in FIG. 10(a);
- FIG. 11 is a partial perspective view of detail B of FIG. 9(a);
- FIG. 12 is a partial perspective view of detail C of FIG. 10(a);
- FIG. 13 is a perspective view of an embodiment of a rack of the present invention; and
- FIG. 14 is a side view of an embodiment of a rack-and pinion assembly of the present invention.
- Referring now to the drawings for the purpose of illustrating the invention and not for the purpose of limiting the same, FIGS.1(a) and (b) are isometric views of the driving components of a
portable planer 40 and their connections according to one embodiment of the invention. Amotor 50 drives, by means of belt and pulley system generally designated 70, aninput shaft 65 on which aconventional cutterhead 60 is mounted, either as an integral piece, or as a separate component. Theinput shaft 65 provides input to a multiple-speed gearbox 80. After speed reduction in thegearbox 80, an output speed is transmitted to afirst feed roller 90 through a first sprocket and chain system generally designated as 95. In this embodiment, thefirst feed roller 90 is the outfeed roller. A second sprocket and chain system generally designated as 105 transmits the same output speed from thefirst feed roller 90 to asecond feed roller 100. Anactuator 115 operates a tab 165 (shown in FIG. 3) that moves in one of two positions corresponding to a first or second output speed. Thetab 165 may also have a neutral position, whereat no output speed is provided. The movement of thetab 165 is controlled by a rack andpinion assembly 120, which is connected to theactuator 115. - In this embodiment, the
gearbox 80 is supported between afirst plate 130 and asecond plate 132, which are separated by a plurality ofspacers 145. Eachspacer 145 comprises ahollow pin 146 that has acapscrew 147 extending therethrough to be threadedly received in a threadedbore 149 inplate 132. See FIG. 4. Afirst input gear 170 may be integrally formed with afirst shaft stem 178 that is rotatably supported in abearing sleeve 179 pressed into ahole 133 in thesecond plate 132 and asecond shaft stem 181 that is rotatably supported in abearing sleeve 185 that is pressed intohole 183 in thefirst plate 130. See FIG. 3.Shaft stem 178 defines afirst axis 148. Asecond input gear 175 is also keyed on thefirst shaft stem 178 so that thefirst input gear 170 and thesecond input gear 175 rotate with the same speed about thefirst axis 148. It will be appreciated that other methods of connecting thefirst input gear 170 and thesecond input gear 175 are within the purview of the person of ordinary skill in the art. A third input gear (drive gear) 182 is attached to theinput shaft 65 and meshingly engages thesecond input gear 175. The number of teeth of thefirst input gear 170, thesecond input gear 175 and thethird input gear 182 are n1, n2, n3 respectively. Denoting the speed of the input shaft by ωis, the common speed of thefirst input gear 170 and thesecond input gear 175 is (n3/n2)ωis. - The
first input gear 170 engages themiddle gear 158 of a three-gear set generally designated as 160. In addition to themiddle gear 158, the three-gear set 160 includes a firstouter gear 155 and a secondouter gear 150. In the embodiment shown in FIGS. 3 and 5, the secondouter gear 150 includes athird shaft stem 159. The firstouter gear 155 and themiddle gear 158 may comprise anintegral assembly 157, which is attached to thethird shaft stem 159 to form the three-gear set 160. See FIG. 5. This arrangement results in a common rotational speed for all three gears of the three-gear set 160 about asecond axis 162, and is one of many arrangements that may be used to achieve the same effect. Denoting by nm the number of teeth of themiddle gear 158 of the three-gear set, the speed of the three-gear set ωim, which is defined as the input speed ωim, is - ωim=(n 1 /n m)(n 3 /n 2)ωis
- The first
outer gear 155 engages afirst output gear 135 and theouter gear 150 engages asecond output gear 137 so that when theinput shaft 65 rotates with a speed ωis, thefirst output gear 135 rotates with a speed ωo1 and thesecond output gear 137 rotates with good speed ωo2: - ωo1=(n 1m /n o1)ωim=(n 1m /n o1)(n 1 /n m)(n 3 /n 2)ωis,
- ωo2=(n 2m /n o2)ωim=(n 2m /n o2)(n 1 /n m)(n 3 /n 2)ωis,
- where n1m is the number of teeth of the first
outer gear 155, n2m is the number of teeth of the secondouter gear 150, no1 is the number of teeth of thefirst output gear 135, and no2 is the number of teeth of thesecond output gear 137. A kinematic requirement for gear engagement is satisfied when the number of teeth is chosen to satisfy the following equation: - n o1 +n 1m =n o2 +n 2m,
- i.e. the sum of the number of teeth of the first outer gear and the first output gear is equal to the sum of the number of teeth of the second outer gear and the second output gear. The
first output gear 135 and thesecond output gear 137 are mounted on anoutput shaft 138 so that they may rotate independently about theoutput shaft 138. Theoutput shaft 138 may rotate with a first speed equal to ωo1 when it is engaged with thefirst output gear 135, as shown in FIG. 3, and with a second speed equal to ωo2 when it is engaged with thesecond output gear 137, as shown in FIG. 4. Theoutput shaft 138 has afirst shaft portion 139 upon which anoutput sprocket 140 may be keyed. Thefirst shaft portion 139 is rotatably supported by aconventional bearing 142 that is pressed into aboss 131 formed in thefirst plate 130. Theoutput shaft 138 further has asecond shaft portion 141 that is rotatably supported in aflanged bearing 143 that is pressed intohole 133 in thesecond plate 132. - The selective engagement of the
output shaft 138 with thefirst output gear 135 or thesecond output gear 137 is accomplished by a gear shifting mechanism, which includes anactuator 115 and atab 165, as shown in FIGS. 3, 4 and 6-8. Afirst end 188 of theactuator 115 is slidably inserted into acylindrical bore 190 coaxially provided in theoutput shaft 138. Theactuator 115 is slidably restrained in thebore 190 by thetab 165, which is fitted through anopening 192 in thefirst end 188 of theactuator 115 so that thetab 165 forms a right angle with theaxis 194 of theactuator 115. See FIG. 6(a). Thetab 165 passes through and extends transversely outward from two diametrically opposedlongitudinal slots 186 in theoutput shaft 138, theslots 186 being aligned with theopening 192 of thefirst end 188 of theactuator 115. See FIGS. 3 and 4. - The
tab 165 may fit into adiametrical slot 194 formed in thehub 200 of thefirst output gear 135 by two semi-cylindricalfirst segments 198, as shown in FIGS. 9(a) and (b). Thetop surface 202 of each of the semi-cylindricalfirst segments 198, forms a first spiral ramp generally designated as 201, so that moving in a counterclockwise direction along thetop surface 202 from one segment to the other (represented by arrow “D” in FIG. 11), there is a ramp-down step 204 (a step in a direction away from the second output gear and toward the first output gear), as shown exaggeratingly in FIG. 11, which is a perspective view of detail B of FIG. 9(b). - The
tab 165 may similarly fit into adiametrical slot 196 formed in thehub 206 of thesecond output gear 137 by twosemi-cylindrical segments 208, as shown in FIGS. 10(a) and (b). Thetop surface 210 of eachsemi-cylindrical segments 208, forms a second spiral ramp generally designated 209, so that moving in a counterclockwise direction along thetop surface 210 from one segment to the other (represented by arrow “E” in FIG. 12), there is a ramp-up step 212 (a step in a direction away from the first output gear and toward the second output gear), as shown exaggeratingly in FIG. 12, which is a perspective view of detail C in FIG. 10(b). - The spiral ramps201 and 209 in the
hubs tab 165 with therespective slots actuator 115. For example, when theactuator 115 is axially moved in a first direction represented by arrow “F” in FIG. 3 thetab 165 contacts thefirst spiral ramp 201. Further axial movement of the actuator shaft in the “F” direction causes the actuator to also rotate in the same direction as thefirst output gear 135 untiltab 165 slides into theslot 194 in thefirst output gear 135 thereby non-rotatably affixing thefirst output gear 135 to theoutput shaft 138 so that the output shaft rotates 138 rotates with the first speed ω1. Thus, when the actuator shaft is moved a predetermined distance, which may be about 8-10 mm in this embodiment, in the first axial direction, the first output gear is non-rotatably affixed to theoutput shaft 138. When in this position, as shown in FIG. 3, those of ordinary skill in the art will appreciate that rotating of thefirst output gear 135 imparts rotary motion to theoutput shaft 138 andoutput sprocket 140 which is attached thereto. Similarly, when theactuator 115 is moved in a second axial direction, thetab 165 contacts thesecond ramp 209 in thehub 206 of the second output gear 137 (typically passing through a neutral position, i.e. a position of no engagement), the spiral ramp formed by thetop surface 210 of thesegments 208 of thesecond output gear 137 guides thetab 165 into theslot 196 of thesecond output gear 137 to a second position of engagement, so that theoutput shaft 138 rotates with the second speed ωo2. Thus, when in the actuator shaft is moved a predetermined distance, which may be about 8-10 mm in this embodiment, in the second axial direction, thesecond output gear 137 is non-rotatably affixed to theoutput shaft 138. It will be appreciated that other methods of shifting between the first and second output gears could be employed without departing from the spirit and scope of the present invention. - As seen from FIGS. 3 and 4 the arrangement of the various gears is such that the
gearbox 80 is compact in size with all the gears confined between the first andsecond gear plates output sprocket 140 is keyed ontooutput shaft 138. Afirst drive chain 97 is received on theoutput sprocket 140 and on afirst sprocket 99 that is keyed on to the shaft of thefirst feed roller 90. Theoutput sprocket 140, thefirst drive chain 97 and thefirst sprocket 99 form the first sprocket andchain system 95. A second sprocket andchain system 105 includes ansecond sprocket 102 keyed onto the shaft of thefirst feed roller 90, athird sprocket 103 keyed onto the shaft of thesecond feed roller 100 and asecond drive chain 104 received on the second andthird sprockets - The gears of the gearbox may be molded from a plastic material, which as will be appreciated can provide advantages of sound and weight reduction, or, alternatively, may be custom-made from powdered metal or cut metal, for superior strength and wear.
- In one embodiment of the
gearbox 80 that may be advantageously used in the power train of 13″ portable planer, the speed reduction ratio in the gearbox is: - ωo1/ωis=(n 1m /n o1)(n 1 /n m)(n 3 /n 2)=(17/75)(12/58)(12/52)≅0.01
- for the first (high speed) and
- ωo2/ωis=(n 2m /n o2)(n 1 /n m)(n 3 /n 2)=(12/80)(12/58)(12/52)≅0.007
- for the second (low) speed. For an input shaft speed, ωis, of 8000 rpm, for example, the first output speed is about 80 rpm and the second output speed is about 56 rpm. With ordinary materials and applications the output shaft would operate at the higher first speed, which is 80 rpm in this example. When the workpiece is made of harder wood, such as, for example, maple or hickory, or when a better finish is desirable the output shaft speed is shifted down to the second (low) speed, which is 56 rpm in this example. In this example, the speed of the output shaft may be reduced by approximately 30%. It will be appreciated that additional speed reduction from the output shaft to the first feed roller may be provided by using sprockets of unequal size in the first sprocket and chain system 96, which transmits rotational motion from the
output shaft 138 to thefirst feed roller 90. The additional reduction may be, for example, at a ratio of 8:11. - The
actuator 115 may be manually operated using ahandle 222 connected to a rack-and-pinion assembly 120, as shown in FIGS. 1(a), 1(b), 13 and 14. Therack 125 is a cylindrical sleeve that is riding on theactuator 115 and prevented from sliding off by a screw or retaining ring at one end. On one side of the surface of therack 125 there is a series ofrack teeth 214 for engaging the teeth of apinion 220. On another side on the surface of therack 125, threegrooves 216 may be provided, each groove corresponding to one of the three positions of theactuator 115, i.e. the first position of engagement, the second position of engagement and the neutral position. A spring-biasedplunger 218 may be used to secure the position of the actuator 115 from accidental disengagement. Ahandle 222 is attached to thepinion 220 and is used to advance therack 125 and theactuator 115, and theplunger 218 locks the actuator in the desired position. It may be appreciated that other means of controlling and locking the motion of the actuator are within the purview of the person of ordinary skill in the art. - The multiple-
speed gearbox 80 has been described in connection with a portable planer, but it can be readily used with a combination planer/shaper, planer/molder, planer/sander, or with any other portable power tool in which a multiple-speed output is desirable. In such a power tool, the input shaft is generally driven by a motor and the output shaft drives a tool holder, which is specific to the particular power tool. - Whereas particular embodiments of the invention have been described herein for the purpose of illustrating the invention and not for the purpose of limiting the same, it will be appreciated by those of ordinary skill in the art that numerous variations of the details, materials and arrangement of parts may be made within the principle and scope of the invention without departing from the invention as described in the appended claims.
Claims (43)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/782,453 US6502475B2 (en) | 2001-02-13 | 2001-02-13 | Multiple-speed gear arrangement for portable planer and other power tools |
CA002368591A CA2368591A1 (en) | 2001-02-13 | 2002-01-18 | Multiple-speed gear arrangement for portable planer and other power tools |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/782,453 US6502475B2 (en) | 2001-02-13 | 2001-02-13 | Multiple-speed gear arrangement for portable planer and other power tools |
Publications (2)
Publication Number | Publication Date |
---|---|
US20020108458A1 true US20020108458A1 (en) | 2002-08-15 |
US6502475B2 US6502475B2 (en) | 2003-01-07 |
Family
ID=25126102
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/782,453 Expired - Fee Related US6502475B2 (en) | 2001-02-13 | 2001-02-13 | Multiple-speed gear arrangement for portable planer and other power tools |
Country Status (2)
Country | Link |
---|---|
US (1) | US6502475B2 (en) |
CA (1) | CA2368591A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2411619A (en) * | 2004-03-02 | 2005-09-07 | Black & Decker Inc | Planer and thicknesser |
US20100206686A1 (en) * | 2009-02-18 | 2010-08-19 | Xerox Corporation | Gearbox Output Switcher |
CN113933555A (en) * | 2021-11-10 | 2022-01-14 | 国网山东省电力公司高密市供电公司 | Electric energy meter mounting and dismounting device |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6951231B2 (en) | 2001-07-30 | 2005-10-04 | Black And Decker, Inc. | Planer apparatus |
US20080072998A1 (en) * | 2006-09-25 | 2008-03-27 | Bor-Yann Chuang | Adjusting and shifting device for a motor base of a planer |
GB0710034D0 (en) * | 2007-05-25 | 2007-07-04 | Gmca Pty Ltd | Improved planer |
CN110500387B (en) * | 2019-08-28 | 2020-08-28 | 徐州锦程行星传动有限公司 | Speed reducer capable of regulating and controlling rotating speed |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2545053A (en) * | 1948-02-26 | 1951-03-13 | Leblond Mach Tool Co R K | Lathe transmission and control mechanism |
US2630846A (en) * | 1949-08-30 | 1953-03-10 | James S Ballantine | Air circulating casing for planing machines |
US2792036A (en) * | 1951-10-08 | 1957-05-14 | Rockwell Mfg Co | Planer and attachments therefor |
US3534607A (en) * | 1968-09-26 | 1970-10-20 | Int Harvester Co | Sliding tube change-speed transmission |
US3913642A (en) * | 1974-12-23 | 1975-10-21 | Airko Manufacturing Company | Wood cutting apparatus |
JPS5915765B2 (en) * | 1981-10-05 | 1984-04-11 | 松下電工株式会社 | Rotary power tool gearbox |
US4559846A (en) * | 1983-11-10 | 1985-12-24 | Dana Corporation | System for shifting a vehicle to two or four-wheel drive |
US4710071A (en) | 1986-05-16 | 1987-12-01 | Black & Decker Inc. | Family of electric drills and two-speed gear box therefor |
US4964313A (en) | 1988-10-24 | 1990-10-23 | Eaton Corporation | Two-speed gear train assembly |
DE69114664T2 (en) * | 1990-08-30 | 1996-05-15 | Ryobi Ltd | Automatic planing machine. |
DE4114818C2 (en) * | 1991-05-07 | 1999-01-07 | Martin Otto Maschbau Gmbh | Device on multi-sided planing machines |
US5588930A (en) | 1995-03-21 | 1996-12-31 | Industrial Technology Research Institute | Two-speed gearbox |
US5904192A (en) * | 1998-08-25 | 1999-05-18 | Chen; Chin-Te | Wood planing machine |
-
2001
- 2001-02-13 US US09/782,453 patent/US6502475B2/en not_active Expired - Fee Related
-
2002
- 2002-01-18 CA CA002368591A patent/CA2368591A1/en not_active Abandoned
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2411619A (en) * | 2004-03-02 | 2005-09-07 | Black & Decker Inc | Planer and thicknesser |
US20050194063A1 (en) * | 2004-03-02 | 2005-09-08 | Marcello Bettacchini | Planer & thicknesser |
US20080105333A1 (en) * | 2004-03-02 | 2008-05-08 | Marcello Bettacchini | Planer and thicknesser |
US7527080B2 (en) | 2004-03-02 | 2009-05-05 | Black & Decker Inc. | Planer and thicknesser |
US7588063B2 (en) | 2004-03-02 | 2009-09-15 | Black & Decker Inc. | Planer and thicknesser |
US20100206686A1 (en) * | 2009-02-18 | 2010-08-19 | Xerox Corporation | Gearbox Output Switcher |
US8534151B2 (en) * | 2009-02-18 | 2013-09-17 | Xerox Corporation | Gearbox output switcher |
CN113933555A (en) * | 2021-11-10 | 2022-01-14 | 国网山东省电力公司高密市供电公司 | Electric energy meter mounting and dismounting device |
Also Published As
Publication number | Publication date |
---|---|
US6502475B2 (en) | 2003-01-07 |
CA2368591A1 (en) | 2002-08-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9636818B2 (en) | Multi-speed cycloidal transmission | |
US8689449B2 (en) | Powered tube cutter | |
US5287786A (en) | Portable electric cutting and scoring saw | |
US20020185289A1 (en) | Elbow attachment | |
US7676934B2 (en) | Keyless adjusting mechanism for chain saw | |
US6502475B2 (en) | Multiple-speed gear arrangement for portable planer and other power tools | |
AU2005229769A1 (en) | Table for band saw | |
US7556069B2 (en) | Adjusting device for the conveying belt of a planer | |
EP1574306B1 (en) | Surface planer | |
GB2412703A (en) | Transmission with gear moved axially by threaded portions on shaft | |
US6802234B2 (en) | Transmission mechanism of drilling/milling tool | |
NL8005097A (en) | MOTOR DRIVE TOOL. | |
US20210197332A1 (en) | Transmission structure of woodworking lathe | |
US195085A (en) | Improvement in bench-drills | |
US7458402B2 (en) | Portable power planer | |
US7013938B2 (en) | Shiftable rolling feed device for a wood planing machine | |
US6666241B1 (en) | Wood planing device for a wood planing machine | |
CN2553977Y (en) | Rotating cutting machine without clamping axle | |
KR20030025562A (en) | Wood Processing Machine | |
KR200260259Y1 (en) | Wood Processing Machine | |
CA2358021A1 (en) | Reversible gear box for use with an auger | |
ITMI20030034U1 (en) | PORTABLE TOOL OPERATED BY MOTOR TO MAKE GROOVES IN WALL OR SIMILAR WORKS |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: DELTA INTERNATIONAL MACHINERY CORP., TENNESSEE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:GARCIA, JAIME E.;ROE, VANCE E.;REEL/FRAME:011556/0527 Effective date: 20010212 |
|
CC | Certificate of correction | ||
AS | Assignment |
Owner name: BLACK & DECKER INC., DELAWARE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:DELTA INTERNATIONAL MACHINERY CORPORATION;REEL/FRAME:016069/0180 Effective date: 20041002 |
|
FPAY | Fee payment |
Year of fee payment: 4 |
|
FEPP | Fee payment procedure |
Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
FPAY | Fee payment |
Year of fee payment: 8 |
|
REMI | Maintenance fee reminder mailed | ||
LAPS | Lapse for failure to pay maintenance fees | ||
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 20150107 |